JP5282770B2 - Hydraulic control device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent at least one of the gear ratio or the torque capacity of a power transmission device from varying when starting pressure accumulation control. <P>SOLUTION: A hydraulic control device includes: a power transmission device configured to be able to change the torque capacity or the gear ratio thereof by hydraulic pressure; a hydraulic pump for generating the initial pressure for the hydraulic pressure supplied to the power transmission device; and an accumulator for accumulating hydraulic pressure generated by the hydraulic pump and discharging hydraulic pressure. The hydraulic control device is provided with a permission means (step S4) for permitting, when the hydraulic pressure supplied to the power transmission device does not increase even after control has been initiated to accumulate hydraulic pressure from the hydraulic pump in the accumulator, control to accumulate discharge hydraulic pressure from the hydraulic pump in the accumulator. <P>COPYRIGHT: (C)2012,JPO&amp;INPIT

Description

  The present invention relates to a hydraulic control apparatus capable of controlling a torque capacity transmission ratio of a power transmission device by hydraulic pressure generated by a hydraulic pump, while accumulating hydraulic pressure in an accumulator.

  Oil pressure is effective as a means for transmitting power, and is used in various mechanical devices. An oil pump for discharging the oil pressure to be supplied to the oil pressure required part is provided, and the engine or electric motor using the oil pump as a power source It is known to drive by. As described above, when the oil pump is driven by the power of the power source, the load of the power source may be relatively increased depending on the supply state of the hydraulic pressure to the hydraulic pressure required portion. In order to suppress such an increase in the load of the power source, the hydraulic pressure discharged from the oil pump is stored in the accumulator, and the accumulator pressure is maintained even when the power source is stopped and the oil pump is stopped. A hydraulic control device configured to be able to supply a hydraulic pressure required part is known, and an example thereof is described in Patent Document 1.

  The hydraulic control device described in Patent Document 1 supplies oil to a control circuit and a lubrication circuit of a vehicle transmission. The hydraulic control device is provided with an oil pump driven by an electric motor. The oil pump discharge oil passage is connected to the import of the mode select valve. This mode select valve has two out ports. One out port is connected to a lubrication circuit, and the other out port is connected to a pressure accumulating circuit via a check valve. The switching of the mode select valve, that is, the switching for connecting the import to one of the two out-ports is made by the solenoid signal pressure.

  Further, an accumulator is connected to the pressure accumulating circuit, and a hydraulic pressure sensor that detects a pressure accumulating state of the accumulator is provided. A line pressure circuit is connected to the pressure accumulation circuit via a primary modulator valve, and the line pressure circuit is connected to a hydraulic servo via a control valve for shift control. When the hydraulic pressure of the hydraulic servo increases, the clutches that control the transmission gear ratio are engaged, while when the hydraulic servo pressure decreases, the clutches are released.

  In the hydraulic control device described in Patent Document 1, it is determined whether the current mode is the lubrication mode or the pressure accumulation mode, and when it is determined that the current mode is the pressure accumulation mode, the oil pump is driven by the electric motor. At the same time, the mode select valve is switched, and the oil discharged from the oil pump is supplied to the pressure accumulating circuit. In this way, when oil is supplied to the pressure accumulation circuit, pressure is accumulated in the accumulator until the set maximum pressure accumulation time elapses. On the other hand, when it is determined that the lubrication mode is selected, the select valve is switched, and the oil discharged from the oil pump is supplied to the lubrication circuit. An example of a hydraulic control device that controls hydraulic pressure supplied to a friction engagement device such as a clutch and a brake in a vehicle transmission is described in Patent Document 2.

JP 2004-84928 A JP 2008-254511 A

  However, in the invention described in Patent Document 1, when it is determined that the pressure accumulation mode is selected, the mode select valve is switched, and control is performed to supply the oil discharged from the oil pump to the pressure accumulation circuit. When the discharge hydraulic pressure of the pump increases, the hydraulic servo hydraulic pressure may increase. As a result, the engagement pressure of the clutch whose engagement and disengagement is controlled by the hydraulic pressure of the hydraulic servo suddenly increases, which may cause a shock.

  The present invention has been made paying attention to the above technical problem, and at the time of starting the control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator, at least one of the speed ratio or the torque capacity of the power transmission device changes. An object of the present invention is to provide a hydraulic control device capable of suppressing this.

  In order to achieve the above object, the invention according to claim 1 is directed to a power transmission device configured to control at least one of a torque capacity and a gear ratio by a hydraulic pressure supplied via a hydraulic pressure supply path, In a hydraulic control device having a hydraulic pump that generates an original pressure of hydraulic pressure to be supplied to a power transmission device, and an accumulator that selectively performs accumulation and release of hydraulic pressure generated by the hydraulic pump, Provided with permission means for permitting control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator when the hydraulic pressure supplied to the power transmission device does not change even when the control for accumulating the discharge hydraulic pressure in the accumulator is started. It is characterized by being.

  According to a second aspect of the present invention, in addition to the configuration of the first aspect, when control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator is started, it is determined whether or not the hydraulic pressure supplied to the power transmission device changes. And when the permitting unit determines that the hydraulic pressure supplied to the power transmission device does not change even when control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator is started, The hydraulic control apparatus includes a means for permitting control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator.

  According to a third aspect of the present invention, in addition to the configuration of the first aspect, when it is determined that the hydraulic pressure supplied to the power transmission device is changed when control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator is started. The hydraulic control device includes a prohibiting unit that prohibits control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator.

  According to a fourth aspect of the present invention, in addition to the configuration of the second or third aspect, a valve that opens and closes the hydraulic pressure supply path is provided, and the determination means is configured so that the hydraulic pressure supply path is opened by the valve. The hydraulic control device includes means for determining that the hydraulic pressure supplied to the power transmission device changes when control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator is started.

  According to a fifth aspect of the present invention, in addition to the configuration of the first aspect, a valve for controlling a flow rate of the pressure oil passing through the hydraulic pressure supply path is provided, and the permitting unit controls the discharge hydraulic pressure of the hydraulic pump to the accumulator. The hydraulic pressure is controlled when the flow rate of the pressure oil passing through the hydraulic pressure supply path is controlled by controlling the valve so that the hydraulic pressure supplied to the power transmission device does not change even when control for accumulating pressure is started. The hydraulic control device includes means for permitting control for accumulating the discharge hydraulic pressure of the pump in the accumulator.

  According to a sixth aspect of the invention, in addition to the structure of any of the first to fifth aspects, the power transmission device includes an engine that generates power by combustion of fuel, and a drive wheel connected to the engine so as to be able to transmit power. When the vehicle is coasting, the output shaft of the engine and the oil pump are connected so that power can be transmitted. In addition, the fuel cut control for stopping the fuel supply to the engine is performed, and the kinetic energy of the vehicle is transmitted to the hydraulic pump via the output shaft of the engine to control the hydraulic pump. The permission means is configured to use kinetic energy of the vehicle when the vehicle is repulsive and performing the fuel cut control. A hydraulic control device which comprises a means to allow the control for accumulating the discharge hydraulic pressure of the hydraulic pump to be moving in the accumulator.

  According to the first aspect of the present invention, the discharge hydraulic pressure of the hydraulic pump is accumulated in the accumulator when the hydraulic pressure supplied to the power transmission device does not change even when control for accumulating the hydraulic pressure discharged from the hydraulic pump is started. Control is allowed. Therefore, when the control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator is started, it is possible to suppress a change in at least one of the gear ratio and the torque capacity of the power transmission device.

  According to the second aspect of the invention, the same effect as that of the first aspect of the invention can be obtained, and the hydraulic pressure supplied to the power transmission device can be changed even when the control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator is started. When it is determined not to perform the control, the discharge hydraulic pressure of the hydraulic pump is allowed to be stored in the accumulator.

  According to the invention of claim 3, in addition to obtaining the same effect as that of the invention of claim 2, when the control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator is started, the hydraulic pressure supplied to the power transmission device changes. When the determination is made, the control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator is prohibited, so that at least one of the gear ratio and the torque capacity of the power transmission device does not change.

  According to the invention of claim 4, in addition to the same effect as that of the invention of claim 2 or 3, when the control for accumulating the hydraulic pressure in the accumulator is started when the hydraulic pressure supply path is opened by the valve, the power is When it is determined that the hydraulic pressure supplied to the transmission device changes, control for accumulating the hydraulic pressure in the accumulator is prohibited.

  According to the fifth aspect of the invention, in addition to obtaining the same effect as the first aspect of the invention, the hydraulic pressure supplied to the power transmission device does not change even when the control for accumulating the hydraulic pressure in the accumulator is started. When the flow rate of the pressure oil passing through the hydraulic pressure supply path is controlled, control for accumulating the hydraulic pressure in the accumulator is permitted.

  According to the sixth aspect of the invention, in addition to obtaining the same effect as that of any of the first to fifth aspects of the invention, when the vehicle is repulsive and performing fuel cut control, the kinetic energy of the vehicle The control which accumulate | stores the discharge hydraulic pressure of the hydraulic pump driven by this in an accumulator is permitted.

It is a flowchart which shows the example of control which can be performed with the vehicle provided with the hydraulic control apparatus of this invention. It is a schematic diagram which shows the power train of the vehicle provided with the hydraulic control apparatus of this invention. It is a mimetic diagram showing a schematic structure of a hydraulic control device of this invention. It is a flowchart which shows the other example of control which can be performed with the vehicle provided with the hydraulic control apparatus of this invention. It is a flowchart which shows the further example of control which can be performed with the vehicle provided with the hydraulic control apparatus of this invention. It is a figure which shows an example of the map used by step S23 of the flowchart of FIG. It is a figure which shows an example of the other map used by step S23 of the flowchart of FIG.

  The hydraulic control device according to the present invention can be used for machines and devices in various fields such as vehicles, aircraft, ships, and industrial machines. In short, the present invention is applied to a hydraulic control device that supplies / discharges hydraulic pressure to / from a hydraulic chamber of a power transmission device or a hydraulic system configured such that at least one of a gear ratio and torque capacity is controlled by hydraulic pressure. can do. In this invention, “when the hydraulic pressure supplied to the power transmission device does not change even when the control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator is started”, before starting the control for accumulating the hydraulic pressure in the accumulator, This includes both that it is predicted that the hydraulic pressure supplied to the power transmission device does not change, and that the valve is actively controlled so that the hydraulic pressure supplied to the power transmission device does not change.

  Next, the present invention will be described with reference to specific examples. FIG. 2 shows a power train of a vehicle 1 equipped with a hydraulic control device 55 according to the present invention. FIG. 3 shows a hydraulic control device 55 that controls the hydraulic pressure supplied to the power transmission device of the vehicle. It is shown. The vehicle 1 has an engine 2 as a driving power source. A power transmission path from the engine 2 to the drive wheels 3 includes a fluid transmission device 4, a forward / reverse switching device 5, a continuously variable transmission 6, and the like. Is provided. The engine 2 is a power unit that burns fuel and converts the thermal energy into kinetic energy and outputs the same. As the engine 2, an internal combustion engine such as a gasoline engine, a diesel engine, or an LPG engine can be used. .

  The fluid transmission device 4 is a transmission device that transmits power by kinetic energy of fluid between an input element and an output element, and includes a pump impeller 7 as an input element and a turbine runner 8 as an output element. Yes. The pump impeller 7 is connected to a crankshaft 9 that is an output shaft of the engine 2 so that power can be transmitted, and the turbine runner 8 is connected to an input shaft 10 so that power can be transmitted. The input shaft 10 is rotatably provided as an element for transmitting power, and a lock-up clutch 11 for transmitting power by frictional force between the input shaft 10 and the crankshaft 9 is provided. The lockup clutch 11 is configured to be released and engaged by hydraulic control. The fluid transmission device 4 may be either a torque converter that can amplify torque transmitted between the pump impeller 7 and the turbine runner 8 or a fluid coupling that cannot perform torque amplification. In this embodiment, it is assumed that a torque converter is used as the fluid transmission device 4, and hereinafter, the fluid transmission device 4 will be referred to as “torque converter 4” for convenience.

  On the other hand, the forward / reverse switching device 5 is a device for switching the rotational direction of the primary pulley 12 of the continuously variable transmission to forward and reverse with respect to the rotational direction of the input shaft 10. FIG. 2 shows an example in which a double pinion type planetary gear mechanism is used as the forward / reverse switching device 5. The planetary gear mechanism includes a sun gear 13 that rotates integrally with the input shaft 10, and is coaxial with the sun gear 13. The ring gear 14 provided above, the pinion gear 15 meshed with the sun gear 13, the pinion gear 16 meshed with the pinion gear 15 and the ring gear 14, and the carrier 17 holding the pinion gears 15, 16 so as to rotate and revolve. doing. The carrier 17 and the primary pulley 12 are connected so as to rotate integrally.

  A clutch C1 for selectively connecting and releasing the input shaft 10 and the carrier 17 is provided. Further, a brake B1 for selectively fixing the ring gear 14 is provided. The clutch C1 and the brake B1 are friction engagement devices whose engagement and disengagement are controlled by hydraulic control. A hydraulic chamber 18 for controlling the engagement and disengagement of the clutch C1 is provided, and the engagement and release of the brake B1 are provided. A hydraulic chamber 19 is provided for controlling the above. The clutch C1 is engaged when the hydraulic pressure in the hydraulic chamber 18 is increased, and the clutch C1 is released when the hydraulic pressure in the hydraulic chamber 18 decreases. That is, as the hydraulic pressure in the hydraulic chamber 18 increases, the torque capacity of the clutch C1 is increased. In contrast, when the hydraulic pressure in the hydraulic chamber 19 is increased, the brake B1 is engaged, while when the hydraulic pressure in the hydraulic chamber 19 is decreased, the brake B1 is released. That is, the torque capacity of the brake B1 is increased as the hydraulic pressure in the hydraulic chamber 19 increases.

  The specific control of the clutch C1 and the brake B1 will be described. When the D (drive) position is selected, the clutch C1 is engaged and the brake B1 is released. Then, when the engine torque is transmitted to the input shaft 10, both the input shaft 10 and the primary pulley 12 are rotated forward. On the other hand, when the R (reverse) position is selected, the clutch C1 is released and the brake B1 is engaged. Then, when the engine torque is transmitted to the input shaft 10, the ring gear 14 becomes a reaction force element, and the primary pulley 12 rotates in the reverse direction.

  In this way, the engine torque is transmitted to the continuously variable transmission 6. The continuously variable transmission 6 is a belt type that is conventionally known, and a belt 21 is wound around a primary pulley 12 and a secondary pulley 20 to transmit torque between the pulleys 12 and 20, and The gear ratio between the primary pulley 12 and the secondary pulley 20 is changed by changing the winding radius of the belt 21 around the pulleys 12 and 20. More specifically, each of the pulleys 12 and 20 includes a fixed sheave and a movable sheave arranged so as to approach and separate from the fixed sheave, and V between the fixed sheave and the movable sheave. A groove-like belt winding groove is formed. The primary pulley 12 is provided with a hydraulic actuator 22 having a hydraulic chamber for moving the movable sheave back and forth in the direction of its axis. On the other hand, the secondary pulley 20 is provided with a hydraulic actuator 23 having a hydraulic chamber for moving the movable sheave back and forth in the direction of its axis. The hydraulic actuator 23 in the secondary pulley 20 is supplied with a hydraulic pressure that generates a clamping pressure for clamping the belt 21.

  For example, when the hydraulic pressure of the hydraulic actuator 23 decreases, the clamping pressure applied to the belt 21 decreases, and the torque capacity of the continuously variable transmission 6 decreases. In contrast, when the hydraulic pressure of the hydraulic actuator 23 is increased, the clamping pressure applied to the belt 21 is increased, and the torque capacity of the continuously variable transmission 6 is increased. When the hydraulic pressure of the hydraulic actuator 23 is kept constant, the clamping pressure applied to the belt 21 is kept constant, and the torque capacity of the continuously variable transmission 6 is kept constant.

  On the other hand, the hydraulic actuator 22 is supplied with hydraulic pressure for controlling the transmission ratio by changing the winding radius of the belt 21. For example, when the hydraulic pressure of the hydraulic actuator 22 decreases, a shift, that is, a downshift, occurs where the winding radius of the belt 21 in the primary pulley 12 is reduced. On the contrary, when the hydraulic pressure of the hydraulic actuator 22 rises, a shift, that is, an upshift occurs in which the winding radius of the belt 21 in the primary pulley 12 increases. When the hydraulic pressure of the hydraulic actuator 22 is kept constant, the winding radius of the belt 21 in the primary pulley 12 is kept constant, and the speed ratio is kept constant.

  Next, the configuration of the hydraulic control device 55 shown in FIG. 3 will be specifically described. The hydraulic control device 55 shown in FIG. 3 has a hydraulic pump 24 connected to a crankshaft 9 that is an output shaft of the engine 2 so as to be able to transmit power. When the hydraulic pump 24 is driven by the torque of the crankshaft 9, the oil stored in the oil pan 11 is sucked into the hydraulic pump 24 and the pressure oil is discharged from the hydraulic pump 24 to the oil passage 26. A primary regulator valve 27 that opens and closes a path for supplying the pressure oil discharged to the oil path 26 to the torque converter 4 side is provided. The primary regulator valve 27 has an input port 28 and an output port 29, the input port 28 is connected to the oil passage 26, and the oil passage 30 is connected to the output port 29.

  The primary regulator valve 27 is configured such that the spool operates to connect and disconnect the input port 28 and the output port 29, and the operation of the spool is controlled by the output signal of the solenoid valve (pressure accumulation switching solenoid) 31. It is configured to be. For example, when the output signal of the solenoid valve 31 is controlled to an on (On) state in which the pressure is high, the input port 28 and the output port 29 are blocked. On the other hand, when the output signal of the solenoid valve 31 is controlled to an off state where the output signal is low, the input port 28 and the output port 29 are connected. Further, an oil path 32 is provided in parallel with the primary regulator valve 27 and connects the oil path 26 and the oil path 30. The oil passage 32 is provided with an orifice 33.

  Further, a secondary regulator valve 34 that controls the oil pressure of the oil passage 30 is provided. The secondary regulator valve 34 has an input port 35 and drain ports 36 and 37, the input port 35 and the oil passage 30 are connected, and the output port 36 is connected to the lubrication system 39 via the oil passage 38. Has been. The lubrication system 39 is a part that is supplied with oil and is lubricated and cooled. The lubrication system 39 includes a bearing that supports the input shaft 10, the primary pulley 12, the secondary pulley 20, and the like, and a planet that constitutes the forward / reverse switching device 5. A gear mechanism is included. Further, an oil passage 53 that connects the oil passage 30 and the oil passage 38 is provided, and an orifice 54 is provided in the oil passage 53. The drain port 37 is connected to the suction port of the hydraulic pump 24.

  Furthermore, a lockup control valve 40 that controls engagement and release of the lockup clutch 11 is provided in a path from the oil path 30 to the torque converter 4. The lockup control valve 40 is configured such that an output signal of an ON / OFF solenoid valve (not shown) and an output signal of a duty solenoid valve (DSU) (not shown) are input to switch the operation of a spool (not shown). The operation of the spool is switched, the pressure oil supply path is changed, and the engagement and release of the lockup clutch 11 are switched. When the oil pressure in the oil passage 30 is relatively low, the drain ports 36 and 37 are both shut off, and when the oil pressure in the oil passage 30 rises, the secondary regulator valve 34 opens the drain port 36 and the drain port. When 37 is closed and the oil pressure of the oil passage 30 further increases, the drain port 36 and the drain port 37 are both opened.

  On the other hand, an accumulator (pressure accumulator) 43 is connected to the oil passage 26 with a check valve 41 and an oil passage 42 interposed therebetween. The check valve 41 is a one-way valve that opens in the direction in which the pressure oil flows from the hydraulic pump 24 toward the accumulator 43 and closes so as to prevent the flow of pressure oil in the opposite direction. The accumulator 43 is configured to store a piston, an elastic expansion body, and the like pressed by an elastic body in a pressure accumulating chamber (not shown) in a container and store hydraulic pressure with a pressure higher than the elastic force. The accumulator 43 releases the hydraulic pressure stored therein to the oil passage 42 so that the hydraulic pressure can be selectively supplied to at least one of the hydraulic actuators 22 and 23 and the hydraulic chambers 18 and 19. It is configured.

  Next, the configuration of a path for supplying pressure oil to the hydraulic actuators 22 and 23 and the hydraulic chambers 18 and 19 will be described. First, an oil passage 44 connected to the hydraulic actuator 22 is provided, and a supply-side electromagnetic on-off valve PriIn is provided between the oil passage 44 and the oil passage 42. The supply-side electromagnetic on-off valve PriIn has a port through which pressure oil passes. By opening and closing the port by electrically controlling the supply-side electromagnetic on-off valve PriIn, pressure oil is supplied to the hydraulic actuator 22. It is configured to supply and shut off the supply of pressure oil. Similarly, an oil passage 45 connected to the hydraulic actuator 23 is provided, and a supply-side electromagnetic on-off valve SecIn is provided between the oil passage 45 and the oil passage 42. This supply-side electromagnetic on-off valve SecIn has a port through which pressure oil passes, and the supply-side electromagnetic on-off valve SecIn is electrically controlled to open and close the port, thereby supplying the hydraulic actuator 23 with pressure oil. It is configured to supply and shut off the supply of pressure oil.

  Further, an oil passage 46 connected to the hydraulic chambers 18 and 19 is provided, and a supply-side electromagnetic on-off valve CBIn is provided between the oil passage 46 and the oil passage 42. Further, an oil passage 47 connected to the hydraulic chamber 18 is provided, and an oil passage 48 connected to the hydraulic chamber 19 is provided. Further, a manual valve 49 is provided for selectively connecting the oil passage 46 to one of the oil passages 47 and 48, or shutting off the oil passage 46 without connecting it to any of the oil passages 47 and 48. Yes. The manual valve 49 is provided with a drain port (not shown) that connects one of the oil passages 47 and 48 to the oil pan 25.

  Then, the supply side electromagnetic opening / closing valve CBIn is electrically controlled to open / close the port, and the oil passage 46 and the oil passage 47 are connected by the manual valve 49, and the oil passage 46 and the oil passage 48 are shut off. Then, the pressure oil in the oil passage 42 can be supplied to the hydraulic chamber 18, and no pressure oil is supplied to the hydraulic chamber 19. On the other hand, when the oil passage 46 and the oil passage 48 are connected by the manual valve 49 and the oil passage 46 and the oil passage 47 are blocked, the pressure oil in the oil passage 42 is supplied to the hydraulic chamber 19. The hydraulic chamber 18 is not supplied with pressure oil.

  Furthermore, the structure of the path | route which discharges | emits pressure oil from the hydraulic actuators 22 and 23 and the hydraulic chambers 18 and 19 is demonstrated. First, a discharge oil passage 50 branched from the oil passage 44 and connecting the hydraulic actuator 22 to the oil pan 25 is connected. The discharge oil passage 50 is provided with a discharge side electromagnetic on-off valve PriEx. This discharge-side electromagnetic on-off valve PriEx has a port through which pressure oil passes. By opening and closing the port by electrically controlling the discharge-side electromagnetic on-off valve PriEx, pressure oil is discharged from the hydraulic actuator 22. It is comprised so that discharge of pressure oil may be stopped.

  Similarly, a discharge oil passage 51 branched from the oil passage 45 and connecting the hydraulic actuator 23 to the oil pan 25 is connected. The discharge oil passage 51 is provided with a discharge-side electromagnetic on-off valve SecEx. The discharge-side electromagnetic on-off valve SecEx has a port through which pressure oil passes. The discharge-side electromagnetic on-off valve SecEx is electrically controlled to open and close the port, thereby discharging the pressure oil from the hydraulic actuator 23. It is comprised so that discharge of pressure oil may be stopped.

  Further, a discharge oil passage 52 that is branched from the oil passage 46 and connects the hydraulic chambers 18 and 19 to the oil pan 25 is connected. The discharge oil passage 52 is provided with a discharge side electromagnetic opening / closing valve CBEx. The discharge-side electromagnetic on-off valve CBEx has a port through which pressure oil passes, and the discharge-side electromagnetic on-off valve CBEx is electrically controlled to open the port. Is connected, the pressure oil in the hydraulic chamber 18 can be discharged to the oil pan 25. On the other hand, when the discharge side electromagnetic switching valve CBEx is electrically controlled to open the port and the oil passage 46 and the oil passage 48 are connected by the manual valve 49, the pressure oil in the hydraulic chamber 19 is discharged to the oil pan 25. be able to.

  The above-mentioned electromagnetic on-off valves PriIn, SecIn, CBIn, PriEx, SecEx, CBEx are configured to prevent hydraulic leakage even when the port is closed, and are composed of poppet valves and needle valves. ing. For example, a valve element that operates by a magnetic attractive force formed by an electromagnetic coil, a spring that presses the valve element in the opposite direction to the magnetic attractive force, and a valve that is pressed by the spring force and that has a port And a seat portion. These supply-side electromagnetic on-off valves PriIn, SecIn, CBIn and discharge-side electromagnetic on-off valves SecEx, CBEx can control the flow rate of pressure oil through the port by controlling the current flowing to the electromagnetic coil. This is an electromagnetic proportional type flow control valve configured as follows. More specifically, when the energizing current to the electromagnetic coil is zero ampere, the port is closed, while the opening of the port increases as the current energizing the electromagnetic coil becomes relatively high. Is configured to do. Thus, when the opening degree of the port of the electromagnetic on-off valve is controlled, the distribution area of the pressure oil changes.

  Controls the opening / closing of the ports of each of the solenoid on / off valves PriIn, SecIn, CBIn, PriEx, SecEx, CBEx, or controls the opening of the ports of the solenoid on / off valves PriIn, SecIn, CBIn, PriEx, SecEx, CBEx In addition, an electronic control unit 56 is provided for controlling the output of the engine 2, further controlling the gear ratio and torque capacity of the continuously variable transmission 1, and further controlling the engagement and disengagement of the clutch C1 and the brake B1. It has been. The electronic control unit 56 includes a vehicle speed, an accelerator opening, a shift position, an engine speed, an input speed and an output speed of the continuously variable transmission 6, a pressure Pacc of the oil passage 42, a pressure Pin of the hydraulic actuator 22, and a hydraulic pressure. The pressure of the actuator 23, the hydraulic pressure Pcb of the oil passage 46, and signals of sensors and switches for detecting the current to the electromagnetic coils of the electromagnetic on-off valves PriIn, SecIn, CBIn, PriEx, SecEx, CBEx are input.

  The operation of the above-described hydraulic control device 55 will be described. Since the hydraulic pump 24 is connected to the crankshaft 9 of the engine 2, the hydraulic pump 24 is driven to discharge the pressure oil when the crankshaft 9 is rotating. The rotation of the crankshaft 9 is forced by the traveling inertia force of the vehicle 1 by stopping the supply of fuel when the fuel is supplied to the engine 2 and rotating autonomously or when the vehicle 1 is coasting. Occurs in any case where it is rotated. That is, the hydraulic pump 24 rotates to generate hydraulic pressure regardless of whether the engine 2 is driven or the engine brake is driven. The pressure and the amount of oil depend on the specifications of the hydraulic pump 24, the rotation speed of the crankshaft 9 (engine rotation speed), and the torque of the crankshaft 9.

  When the hydraulic pump 24 is driven and pressure oil is discharged to the oil passage 26, when the internal pressure of the accumulator 43 is not less than a predetermined value, it is not necessary to store pressure in the accumulator 43. The oil passage 26 and the oil passage 30 are connected by the control of the valve 27. In this way, when the oil passage 26 and the oil passage 30 are connected, the pressure oil discharged from the hydraulic pump 24 is supplied to the torque converter 4 via the lock-up control valve 40. A part of the pressure oil in the oil passage 39 is also supplied to the lubrication system 39 via the oil passage 53. When the internal pressure of the accumulator 43 exceeds the oil pressure of the oil passage 26, the check valve 41 is closed, so that the discharge hydraulic pressure of the hydraulic pump 24 is not accumulated in the accumulator 43.

  On the other hand, when the hydraulic pump 24 is driven and the pressure oil is discharged, the internal pressure of the accumulator 43 is less than a predetermined value, so that when the pressure needs to be stored in the accumulator 43, the primary regulator valve By the control of 27, the oil passage 26 and the oil passage 30 are blocked. Then, the hydraulic pressure of the oil passage 26 is increased by the discharge hydraulic pressure of the hydraulic pump 24 and the check valve 41 is opened, and the pressure oil discharged from the hydraulic pump 24 is supplied to the oil passage 42 and accumulated in the accumulator 43. Further, part of the pressure oil in the oil passage 26 is also supplied to the oil passage 30 via the oil passage 32. Note that the predetermined value that serves as a reference for determining whether or not it is necessary to store pressure in the accumulator 43 is determined based on the hydraulic pressure Pacc of the oil passage 42, the required hydraulic pressure in the hydraulic chambers 18 and 19, the required hydraulic pressure in the hydraulic actuators 22 and 23, and the like. This value is stored in advance in the electronic control unit 56.

  Next, control of the torque capacity and the gear ratio of the continuously variable transmission 6 will be described. The torque capacity of the continuously variable transmission 6 is controlled to a capacity capable of sufficiently transmitting the input torque, and this is set by the clamping pressure corresponding to the hydraulic pressure supplied to the hydraulic actuator 23 of the secondary pulley 20. More specifically, the clamping pressure is controlled according to the required driving force obtained based on the accelerator opening, the throttle opening, etc., and when the required driving force is large, the hydraulic pressure supplied to the hydraulic actuator 23 is high. It is controlled to become. In the hydraulic control device 55 shown in FIG. 3, the control is performed by opening the port of the supply side electromagnetic on-off valve SecIn communicating with the hydraulic actuator 23 and closing the port of the discharge side on-off valve SecEx, from the accumulator 23 to the hydraulic actuator. This is done by supplying hydraulic pressure to 22. At this time, the flow rate of the pressure oil passing through the port of the supply-side electromagnetic on-off valve SecIn serving as the pressure oil supply path is controlled by the target pressure (or target clamping pressure) in the hydraulic actuator 23 of the secondary pulley 20 and the hydraulic actuator 23. This can be done based on actual hydraulic pressure.

  On the other hand, when the pinching pressure is reduced based on the decrease in the input torque to the continuously variable transmission 6, the port of the discharge side electromagnetic on-off valve SecEx connected to the hydraulic actuator 23 of the secondary pulley 20 is opened, and The port of the supply side electromagnetic opening / closing valve SecIn is closed, and the pressure oil of the hydraulic actuator 23 is drained to the oil pan 25 via the discharge side oil passage 51. At this time, the flow rate of the pressure oil passing through the port of the discharge side electromagnetic on-off valve SecEx serving as the pressure oil discharge path is controlled by the target pressure (or target clamping pressure) in the hydraulic actuator 23 of the secondary pulley 20 and the hydraulic actuator 23 thereof. This can be done on the basis of the actual hydraulic pressure at.

  Further, the gear ratio by the continuously variable transmission 6 is obtained from the shift map based on the required drive amount such as the accelerator opening and the vehicle speed or the turbine speed. Therefore, the groove width of the primary pulley 12 is controlled so as to be the target gear ratio. The control is performed by supplying and discharging pressure oil to and from the hydraulic actuator 22 in the primary pulley 12. Specifically, the port of the supply side electromagnetic on-off valve PriIn and the port of the discharge side electromagnetic on-off valve PriEx are opened and closed. Is done. For example, when the gear ratio of the continuously variable transmission 6 is relatively reduced (upshift), the port of the supply side electromagnetic on-off valve PriIn is opened and the port of the discharge side electromagnetic on-off valve PriEx is closed, so that the hydraulic actuator Pressure oil is supplied to 22. In this way, when the oil amount of the hydraulic actuator 22 increases, the pressure Pin of the hydraulic chamber of the hydraulic actuator 22 increases and the groove width of the primary pulley 12 is narrowed.

  On the contrary, when the gear ratio of the continuously variable transmission 6 is relatively increased (downshift), the port of the discharge side electromagnetic on-off valve PriEx is opened and the port of the supply side electromagnetic on-off valve PriIn is closed. Thus, the oil in the hydraulic actuator 22 is drained to the oil pan 25. In this way, when the oil amount of the hydraulic actuator 22 decreases and the pressure Pin of the hydraulic chamber of the hydraulic actuator 22 decreases, the groove width of the primary pulley 12 is relatively widened by the tension of the belt 21.

  As described above, the opening / closing control of the supply-side electromagnetic on-off valve PriIn and the discharge-side electromagnetic on-off valve PriEx for controlling the transmission ratio of the continuously variable transmission 6 is performed by the stroke amount of the movable sheave constituting the primary pulley 12 or the stepless control. This may be performed based on the comparison result between the actual transmission ratio, which is the ratio between the input rotation speed and the output rotation speed of the transmission 6, and the target transmission ratio, or the comparison result between the pressures of the hydraulic actuator 22 and the hydraulic actuator 23. it can.

  In a steady running state where the accelerator opening and the vehicle speed are maintained substantially constant, the transmission ratio and the clamping pressure of the continuously variable transmission 6 are maintained constant. In that case, the ports of the electromagnetic on-off valves PriIn, PriEx, SecIn, SecEx are all closed and pressure oil is sealed in the hydraulic actuators 22, 23. In this state, there is no leakage of hydraulic pressure from the electromagnetic on-off valves PriIn, PriEx, SecIn, SecEx, so that the hydraulic pressure stored in the accumulator 43 decreases or the accumulator is maintained to maintain the pressure of the hydraulic actuators 22, 23. Therefore, it is not necessary to continuously supply the hydraulic pressure from 43, so that no energy loss occurs due to leakage of the hydraulic pressure.

  Further, control of the clutch C1 and the brake B1 will be described. When the shift position detected by the electronic control unit 56 is the D position, control for engaging the clutch C1 and releasing the brake B1 is performed. Specifically, the port of the supply side electromagnetic on-off valve CBIn is opened, and the discharge side electromagnetic on-off valve CBEx is closed. Further, the oil passage 46 and the oil passage 47 are connected by the manual valve 49, and the oil passage 46 and the oil passage 47 are blocked. Then, the pressure in the accumulator 43 is supplied to the hydraulic chamber 18 via the oil passage 46 and the oil passage 46, the hydraulic pressure in the hydraulic chamber 18 rises, the clutch C1 is engaged, and the pressure oil in the hydraulic chamber 19 is The brake is discharged from the drain port of the manual valve 49 and the brake B1 is released.

  On the other hand, when the R position is detected as the shift position, the clutch C1 is released and the brake B1 is engaged. Specifically, the port of the supply side electromagnetic on-off valve CBIn is opened, and the discharge side electromagnetic on-off valve CBEx is closed. Further, the oil passage 46 and the oil passage 48 are connected by the manual valve 49, and the oil passage 46 and the oil passage 47 are shut off. Then, the hydraulic pressure in the accumulator 43 is supplied to the hydraulic chamber 19 via the oil passage 42 and the oil passage 46, and the hydraulic pressure in the hydraulic chamber 19 increases and the brake B1 is engaged. On the other hand, the pressure oil in the hydraulic chamber 18 is discharged from the drain port of the manual valve 49, and the clutch C1 is released.

  On the other hand, when the N (neutral) position or the P (parking) position is selected as the shift position, the port of the supply side electromagnetic on-off valve CBIn is closed and the port of the discharge side electromagnetic on-off valve CBEx is opened, By switching the manual valve 49, the oil passages 47, 48 are both connected to the oil passage 46, and the pressure oil in the hydraulic chambers 18, 19 is discharged to the oil pan 25 via the oil passages 46, 52, and the brake B1 and the clutch C1 is released together.

  When the clutch C1 or the brake B1 is engaged, the port of the supply side electromagnetic on-off valve CBIn is closed, and the port of the discharge side electromagnetic on-off valve CBEx is closed, the hydraulic chamber 18 or the hydraulic chamber When the pressure oil of 19 leaks through the manual valve 49, the port of the supply side electromagnetic on-off valve CBIn is opened and the hydraulic pressure of the accumulator 43 is supplied to the hydraulic chamber 18 or the hydraulic chamber 19, thereby A decrease in hydraulic pressure can be suppressed.

  As described above, in the vehicle 1 including the hydraulic control device 55 of FIG. 3, the pressure accumulated in the accumulator 43 can be released and supplied to the hydraulic actuators 22 and 23 and the hydraulic chambers 18 and 19. In addition, in the vehicle 1 shown in FIG. 3, fuel cut control can be executed in addition to control for supplying the fuel to the engine 2 and burning it to cause the engine 2 to autonomously rotate. For example, when the vehicle 1 is coasting, kinetic energy is transmitted to the engine 2 and the engine 2 is rotated. Therefore, the fuel supply is stopped and the engine 2 is idled, while the vehicle speed is reduced and the engine 2 is rotated. When the rotation speed becomes equal to or lower than the predetermined rotation speed, the supply of fuel is started to burn the fuel, and the engine 2 can be rotated autonomously. Thus, the fuel cut control is to stop the supply of fuel to the engine 2 when the engine 2 is rotated by the kinetic energy generated by the repulsive running of the vehicle 1.

  In this embodiment, since the hydraulic pump 24 is connected to the crankshaft 9 so as to be able to transmit power, when the engine 2 rotates autonomously, the hydraulic pump 24 is driven by the torque, and the fuel is being cut. Alternatively, the kinetic energy of the vehicle 1 can be transmitted to the crankshaft 9 and the hydraulic pump 24 can be driven by the torque of the crankshaft 9. Furthermore, in this embodiment, various kinds of control can be executed when accumulating the hydraulic pressure of the pressure oil discharged from the hydraulic pump 24 in the accumulator 43, and the control examples will be sequentially described.

(First control example)
A first control example that can be executed in the vehicle 1 having the hydraulic control device 55 shown in FIG. 3 will be described with reference to the flowchart of FIG. First, it is determined whether or not fuel cut control is being executed (step S1). Fuel cut control is being executed, for example, the accelerator opening is fully closed, the engine speed is greater than or equal to a predetermined value, the vehicle speed is greater than or equal to a predetermined value, fuel injection is stopped, etc. When all are detected, the fuel cut control is being executed. If the determination in step S1 is affirmative, the current supplied to the electromagnetic coils of the supply-side electromagnetic on-off valves PriIn, SecIn, CBIn is detected (step S2), and all currents are “zero” amperes. Is determined (step S3).

  Steps S2 and S3 are processes for indirectly determining from the current whether all the ports of the supply side electromagnetic opening / closing valves PriIn, SecIn, and CBIn are closed or open. If the determination in step S3 is affirmative, all the ports of the supply side electromagnetic on-off valves PriIn, SecIn, CBIn are closed. Therefore, if an affirmative determination is made in step S3, the pressure accumulation permission flag is turned on (step S4), and the process returns to step S1. In other words, a positive determination in step S3 means that even if the discharge hydraulic pressure of the hydraulic pump 24 changes, the change in hydraulic pressure is transmitted to either the hydraulic actuators 22 and 23 or the hydraulic chambers 18 and 19. Therefore, the pressure accumulation permission flag is turned on (On) in step S4.

  As described above, when the internal pressure of the accumulator 24 becomes less than a predetermined value when the pressure accumulation permission flag is turned on and the pressure needs to be accumulated in the accumulator 43, the input port 28 and the output port 29 of the primary regulator valve 27 Can be controlled by accumulating the hydraulic pressure discharged from the hydraulic pump 24 in the accumulator 43. Further, when the pressure accumulation control is performed, the ports of the supply side electromagnetic on-off valves PriIn, SecIn, CBIn are all closed, so even if the discharge hydraulic pressure of the hydraulic pump 24 rises, the hydraulic pressure of the hydraulic actuators 22, 23, or the hydraulic chamber An increase (change) in the hydraulic pressures 18 and 19 can be avoided. Therefore, it can be suppressed that the driving force of the vehicle 1 is abruptly changed due to an increase in hydraulic pressure and is felt as a shock.

  On the other hand, a negative determination in step S3 means that at least one of the ports of the supply-side electromagnetic on-off valves PriIn, SecIn, CBIn is open. For example, when the port of the supply side electromagnetic on-off valve PriIn is opened in order to execute an upshift that relatively increases the hydraulic pressure of the hydraulic actuator 22 to relatively reduce the transmission ratio of the continuously variable transmission 6, A negative determination is made in step S3. Further, in order to execute control for relatively increasing the hydraulic pressure of the hydraulic actuator 23, a negative determination is made in step S3 that the port of the supply-side electromagnetic on-off valve SecIn is open. Further, when the port of the supply-side electromagnetic on-off valve CBIn is opened in order to prevent a decrease in hydraulic pressure due to pressure oil leakage in the hydraulic chamber 18 or the hydraulic chamber 19, a negative determination is made in step S3.

  As described above, when the negative determination is made in step S3, when the input port 28 and the output port 29 of the primary regulator valve 27 are shut off and the discharge hydraulic pressure of the hydraulic pump 24 is increased, the supply of the port is opened. There is a possibility that the hydraulic pressure of the hydraulic actuators 22 and 23 connected to the side electromagnetic on-off valve or the hydraulic pressure of the hydraulic chambers 18 and 19 may increase. Therefore, if a negative determination is made in step S3, the pressure accumulation permission flag is turned off (step S5), and the process returns to step S1. For this reason, even if the internal pressure of the accumulator 43 becomes less than a predetermined value and it is necessary to store the pressure in the accumulator 43, “the primary regulator valve 27 shuts off the input port 28 and the output port 29 and discharges from the hydraulic pump 24. "Control for accumulating the hydraulic pressure in the accumulator 43" is prohibited. If a negative determination is made in step S1, the process proceeds to step S5.

  As described above, in the flowchart of FIG. 1, if control for accumulating the discharge hydraulic pressure of the hydraulic pump 24 in the accumulator 43 is performed, does the hydraulic pressure of the hydraulic actuators 22 and 23 or the hydraulic pressure of the hydraulic chambers 18 and 19 increase (change)? Whether or not is determined indirectly based on the currents of the supply-side electromagnetic on-off valves PriIn, SecIn, and CBIn. If it is determined that at least one of the hydraulic pressures of the hydraulic actuators 22 and 23 or the hydraulic pressures of the hydraulic chambers 18 and 19 does not increase even if the pressure accumulation control is performed, the pressure accumulation permission flag is turned on. On the other hand, if it is determined that at least one of the hydraulic pressure of the hydraulic actuators 22 and 23 or the hydraulic pressure of the hydraulic chambers 18 and 19 is increased when the pressure accumulation control is performed, the pressure accumulation permission flag is turned off.

  Note that the execution order of steps S1, S2, and S3 shown in the flowchart of FIG. 1 can be changed, or the determinations of steps S1 and S3 can be made simultaneously. In other words, the routine may proceed to step S4 when both of the determinations in steps S1 and S3 are positive, and may proceed to step S5 when the determination is negative in at least one of steps S1 and S3. . Here, the process of step S2 is not performed after the determination of step S3. Thus, even if the execution order of the steps in the flowchart of FIG.

(Second control example)
Next, in the vehicle 1 shown in FIG. 3, another control example that can be performed in relation to the pressure accumulation in the accumulator 43 will be described with reference to the flowchart of FIG. In the flowchart of FIG. 4, steps that perform the same processing as in the flowchart of FIG. 1 are assigned the same step numbers as in the flowchart of FIG. In the flowchart of FIG. 4, following step S2, the gear ratio of the continuously variable transmission 6 is detected (step S11), and the process proceeds to step S3. The transmission ratio of the continuously variable transmission 6 can be obtained from the input rotation speed and the output rotation speed.

  If the determination in step S3 is affirmative, it is determined whether or not the speed ratio of the continuously variable transmission 6 is higher than a predetermined value (step S12). Specifically, it is determined whether or not the gear ratio of the continuously variable transmission 6 is smaller than a predetermined value. The meaning of step S12 is as follows. When the pressure accumulation control is executed, the discharge pressure of the hydraulic pump 24 increases, so that the torque necessary for driving the hydraulic pump 24 becomes relatively large. That is, since the hydraulic pump 24 is driven by the kinetic energy when the vehicle 1 is repulsive, the engine braking force is increased. At this time, if the transmission gear ratio of the continuously variable transmission 6 is relatively large, the torque fluctuation range of the drive wheels 3 that occurs as the pressure accumulation control is executed becomes relatively large, and the passenger of the vehicle 1 may be felt as a shock. There is.

  Therefore, in step S12, when the pressure accumulation control is executed while the vehicle 1 is coasting, whether the engine braking force is strengthened and a shock to the extent that the occupant feels is generated. This is indirectly estimated from the transmission ratio. In order to make the determination in step S12, the engine braking force that increases when the pressure accumulation control is started is mapped in advance based on conditions such as the vehicle speed, the gear ratio of the continuously variable transmission 6, the engine speed, and electronically controlled. It is stored in the device 56. If the determination in step S12 is affirmative, it is presumed that the shock does not increase as much as the occupant of the vehicle 1 feels even if the pressure accumulation control is started, and the process proceeds to step S4. On the other hand, if the negative determination is made in step S12, it is estimated that when the pressure accumulation control is executed, the shock is estimated to be large enough to be experienced by the occupant, and thus the process proceeds to step S5.

  When the flowchart of FIG. 4 is executed, the same effect as the flowchart of FIG. 1 can be obtained with respect to a portion that performs the same processing as the flowchart of FIG. In the flowchart of FIG. 4, when switching from “without pressure accumulation control” to “with pressure accumulation control” before switching from “without pressure accumulation control” to “with pressure accumulation control”, the engine braking force is strengthened, and as a shock Estimated whether or not to feel. When switching from “without pressure accumulation control” to “with pressure accumulation control”, when it is estimated that the engine braking force is strengthened and a shock is felt, it is prohibited to start the pressure accumulation control. On the other hand, when switching from “without pressure accumulation control” to “with pressure accumulation control” is estimated not to be felt as a shock even if the engine braking force is strengthened, it is permitted to start the pressure accumulation control.

  Note that the execution order of the steps shown in the flowchart of FIG. 4 can be changed, or the determinations of steps S1, S3, and S12 can be made simultaneously. That is, the routine proceeds to step S4 when both of the determinations in steps S1, S3, and S12 are positive, and proceeds to step S5 when the determination in any of steps S1, S3, and S12 is negative. If it is. Here, the process of step S11 is not performed after the determination of step S12, and the process of step S2 is not performed after the determination of step S3. Thus, even if the execution order of the steps in the flowchart of FIG.

(Third control example)
Next, in the vehicle 1 shown in FIG. 3, another control example that can be performed in relation to the pressure accumulation in the accumulator 43 will be described with reference to the flowchart of FIG. In the flowchart of FIG. 5, steps that perform the same processing as in the flowchart of FIG. 1 or FIG. 4 are given the same step numbers as in the flowchart of FIG. The flowchart of FIG. 5 is executed when the port of the supply side electromagnetic opening / closing valve is open. In the flowchart of FIG. 5, if the determination is affirmative in step S1, the process proceeds to step S12 via step S11. If the determination is affirmative in step S12, the process of step S4 is performed. Further, the signal of the solenoid 31 is detected, specifically, it is detected whether it is turned on (Off) or turned off (Step S21).

  Further, assuming that switching from “without pressure accumulation control” to “with pressure accumulation control” is performed, it is estimated how much the oil pressure Pacc of the oil passage 42 will increase (step S22). . In order to perform the process of step S22, when switching from “without pressure accumulation control” to “with pressure accumulation control”, the data obtained by conducting an experiment or simulation to determine how much the hydraulic pressure Pacc increases is the electronic control unit 56. Is remembered. Furthermore, before and after switching from “without pressure accumulation control” to “with pressure accumulation control”, the port is open so that the flow rate of pressure oil through the port of the supply-side electromagnetic on-off valve that is currently open is the same. A process of changing the current of the supply side electromagnetic opening / closing valve is performed (step S23), and the process returns to step S1.

  As described above, the supply-side electromagnetic opening / closing valve uses a valve configured such that the opening degree of the port increases as the current I increases relatively. When the oil pressure upstream of the supply side electromagnetic on-off valve in the supply direction rises, the flow rate of the pressure oil passing through the port becomes relatively large. That is, as the current I is relatively increased, the flow rate of the pressure oil passing through the port is relatively increased. This will be described with reference to the map of FIG. 6. A solid line indicates a characteristic when the pressure accumulation control is not performed and the differential pressure between the upstream hydraulic pressure and the downstream hydraulic pressure is relatively small. Further, the characteristics when the pressure accumulation control is performed and the differential pressure between the upstream hydraulic pressure and the downstream hydraulic pressure of the supply side electromagnetic opening / closing valve is relatively large are indicated by broken lines. In both of the two characteristics, the flow rate Q of the pressure oil passing through the port increases as the current I increases relatively. Even if the current I is the same, the flow rate Q of the pressure oil passing through the port is greater on the broken line than on the solid line. This is because the differential pressure between the upstream hydraulic pressure and the downstream hydraulic pressure of the supply side electromagnetic opening / closing valve is relatively large.

  Therefore, if the process of reducing the current supplied to the supply-side electromagnetic on-off valve is performed before and after switching from “without pressure accumulation control” to “with pressure accumulation control” in step S23, even if the oil pressure Pacc of the oil passage 42 increases. The flow rate of the pressure oil passing through the port of the supply side electromagnetic opening / closing valve can be made the same. In the flowchart of FIG. 5, if a negative determination is made in step S1 or step S12, the process proceeds to step S5.

  As described above, in the flowchart of FIG. 5, the same effect as the flowchart of FIG. 1 or 4 can be obtained for a portion that performs the same processing as the flowchart of FIG. 1 or 4. Further, in the flowchart of FIG. 5, even if the hydraulic pressure Pacc increases before switching from “without pressure accumulation control” to “with pressure accumulation control”, the hydraulic pressure of the hydraulic actuators 22 and 23 or the hydraulic pressure of the hydraulic chambers 18 and 19 increases. The current of the supply side electromagnetic opening / closing valve is obtained in advance so as not to change.

  Therefore, after the process of step S23 in the flowchart of FIG. 5 is performed, when the port of any of the supply-side electromagnetic on-off valves is open, the internal pressure of the accumulator 43 becomes less than a predetermined value, and the discharge hydraulic pressure of the hydraulic pump 24 is reduced to the accumulator. If it is necessary to store in 43, even if the pressure accumulation control is started and the hydraulic pressure Pacc increases, the hydraulic pressure of the hydraulic actuators 22 and 23 or at least one hydraulic pressure of the hydraulic chambers 18 and 19 can be suppressed from increasing (changing). . Therefore, the area where pressure accumulation control can be started increases. In the flowchart of FIG. 5, the execution order of each step may be changed so that the process proceeds to step S21 when an affirmative determination is made in step S12, and returns via step S4 after step S23. it can.

  In the hydraulic control device 55 shown in FIG. 3, as the supply side electromagnetic on-off valves PriIn, SecIn, CBIn, the ports are opened when the current value is zero ampere, and the ports increase as the current value increases. It is also possible to use an electromagnetic proportional flow control valve (normally open type) configured such that the opening degree of the valve is reduced. More specifically, the valve has a maximum current (Max) and the port is closed. When the flow chart of FIG. 1 is executed when such an electromagnetic proportional flow control valve (normally open type) is used, the current values of the supply side electromagnetic on-off valves PriIn, SecIn, CBIn are all in step S3. It is determined whether or not it is the maximum (Max). If the determination in step S3 is affirmative, the routine proceeds to step S4. If the determination in step S3 is negative, the routine proceeds to step S5. That's fine.

  Similarly, when the electromagnetic proportional flow rate control valve (normally open type) is used as the supply-side electromagnetic on-off valves PriIn, SecIn, CBIn, when the flowchart of FIG. 4 is executed, in step S3, It is determined whether or not the current values of the supply-side electromagnetic shut-off valves PriIn, SecIn, CBIn are all maximum (Max). If the determination in step S3 is affirmative, the process proceeds to step S12, while in step S3. If the determination is negative, the routine may proceed to step S5.

  Further, an example will be described in which the flowchart of FIG. 5 is executed when an electromagnetic proportional flow control valve (normally open type) is used as the supply-side electromagnetic on-off valves PriIn, SecIn, and CBIn. In the supply-side electromagnetic on-off valves PriIn, SecIn, and CBIn, the flow rate Q of the pressure oil passing through the port increases as the current I decreases relatively. More specifically, as shown in the map of FIG. 7, when there is “no pressure accumulation control” and the differential pressure between the upstream hydraulic pressure and the downstream hydraulic pressure is relatively small (solid line) Alternatively, when the pressure accumulation control is performed and the differential pressure between the upstream hydraulic pressure and the downstream hydraulic pressure of the supply side electromagnetic opening / closing valve is relatively large (broken line), the port is increased as the current I is relatively decreased. The flow rate Q of the pressure oil passing through increases. And even if the electric current I is the same, as for the flow volume Q of the pressure oil which passes a port, the broken line becomes more than the solid line. This is because the differential pressure between the upstream hydraulic pressure and the downstream hydraulic pressure of the supply side electromagnetic opening / closing valve is relatively large. For this reason, if the process of increasing the current supplied to the supply-side electromagnetic on / off valve is performed before and after switching from “without pressure accumulation control” to “with pressure accumulation control” in step S23 of FIG. Even if it increases, the flow rate of the pressure oil passing through the port of the supply side electromagnetic opening / closing valve can be made the same.

  Further, in the hydraulic control device 55 shown in FIG. 3, as the supply-side electromagnetic on-off valve, energization and non-energization are alternately repeated, and the duty ratio which is the energization ratio is controlled to control the pressure oil passing through the port. A duty solenoid valve capable of adjusting the flow rate can also be used. When a duty solenoid valve is used as the supply-side electromagnetic on-off valve, energization and de-energization are repeated alternately, and the state in which the pressure oil at a flow rate corresponding to the duty ratio passes through the port is `` port open ''. A state in which the port is always closed while being energized is “port closing”. Then, in the vehicle using the duty solenoid valve as the supply-side electromagnetic opening / closing valve, when the flowchart of FIG. 1 is executed, the duty ratio of each supply-side electromagnetic opening / closing valve is read in step S2. Further, in step S3, it is indirectly determined from the duty ratio whether or not the ports of the supply side electromagnetic on / off valves are always closed. In step S3, all the ports of the supply side electromagnetic on / off valves are always closed. If it is determined that there is a routine, the process proceeds to step S4, and if it is determined in step S3 that the port of at least one supply-side electromagnetic switching valve has been opened or closed, the routine proceeds to step S5.

  Moreover, the flowchart of FIG. 4 can also be performed in the vehicle which uses a duty solenoid valve as a supply side electromagnetic switching valve. Specifically, in step S2, the duty ratio of each supply-side electromagnetic on-off valve is read. Further, in step S3, it is indirectly determined from the duty ratio whether or not the ports of the supply side electromagnetic on / off valves are always closed. In step S3, all the ports of the supply side electromagnetic on / off valves are always closed. If it is determined that there is a routine, the process proceeds to step S12, and if it is determined in step S3 that the port of at least one supply side electromagnetic opening / closing valve has been opened or closed, the routine proceeds to step S5.

  Furthermore, in the vehicle using a duty solenoid valve as the supply-side electromagnetic opening / closing valve, the flowchart of FIG. 5 can be executed. Specifically, in step S23, the flow rate of the pressure oil passing through the port of the supply side electromagnetic opening / closing valve whose port is opened / closed does not change even if the hydraulic pressure Pacc is increased by switching from no pressure accumulation control to with pressure accumulation control. Thus, what is necessary is just to obtain | require the duty ratio of the supply side electromagnetic on-off valve. As described above, the effects of executing the flowcharts of FIGS. 1, 4 and 5 in the vehicle in which either the electromagnetic proportional flow control valve or the duty solenoid valve is used as the supply side electromagnetic opening / closing valve are as follows. It is the same.

  Here, the correspondence between the configuration shown in FIGS. 2 and 3 and the configuration of the present invention will be described. The continuously variable transmission 6 and the forward / reverse switching device 5 correspond to the power transmission device of the present invention. The oil passages 42, 44, 45, 46 correspond to the hydraulic supply path of the present invention, the hydraulic pump 24 corresponds to the hydraulic pump of the present invention, the accumulator 43 corresponds to the accumulator of the present invention, and the supply side electromagnetic The on-off valves PriIn, SecIn, and CBIn correspond to the valves of the present invention, the vehicle 1 corresponds to the vehicle of the present invention, the drive wheels 3 correspond to the drive wheels of the present invention, and the crankshaft 9 corresponds to the present invention. Corresponds to the output shaft.

  In the vehicle 1 shown in FIG. 3, the forward / reverse switching device 5 is provided between the torque converter 4 and the continuously variable transmission 6, but between the continuously variable transmission 6 and the drive wheels 3. Each flowchart can be executed also in a vehicle having a configuration in which a forward / reverse switching device is provided. Further, each flowchart can be executed even in a vehicle including a toroidal-type continuously variable transmission instead of the belt-type continuously variable transmission 6. This toroidal continuously variable transmission has a power roller interposed between an input disk and an output disk, and controls the speed ratio by operating linearly with the power roller supported by a trunnion. On the other hand, the torque capacity is controlled by controlling the clamping force applied to the input disk and the output disk. Then, the hydraulic pressure accumulated in the accumulator may be released and supplied to a hydraulic chamber that linearly operates the power roller or a hydraulic chamber that controls the clamping pressure.

  Furthermore, a stepped transmission capable of changing the gear ratio stepwise is provided between the engine and the drive wheel, and the gear ratio and torque capacity of the stepped transmission are hydraulically controlled. The present invention can also be applied to other vehicles. Such a stepped transmission has a known structure having a plurality of planetary gear mechanisms, a clutch for connecting and releasing rotating elements, and a brake for selectively fixing the rotating elements. Can be mentioned. A hydraulic chamber that controls the engagement and release of the clutch and brake is provided, and the hydraulic pressure supplied to the hydraulic chamber may be supplied from the accumulator.

  The flowchart of FIG. 1 corresponds to the inventions of claims 1 to 4 and claim 6 of the present invention. Correspondence between the functional means shown in the flowchart of FIG. 1 and the configuration of the present invention. Describing the relationship, steps S1 to S3 correspond to determination means of the present invention, step S4 corresponds to permission means of the present invention, and step S5 corresponds to prohibition means of the present invention. Further, the flowchart of FIG. 4 corresponds to the inventions of claims 1 to 4 and claim 6 of the present invention, and the functional means shown in the flowchart of FIG. 4 corresponds to the configuration of the present invention. Describing the relationship, step S4 corresponds to permission means of the present invention, step S5 corresponds to prohibition means of the present invention, and steps S1, S2, S11, S3 correspond to determination means of the present invention. Further, the flowchart of FIG. 5 corresponds to the invention of claims 1, 5 and 6 of the present invention, and the correspondence between the functional means shown in the flowchart of FIG. 5 and the configuration of the present invention will be described. Steps S4, S21, S22, and S23 correspond to permission means of the present invention.

  DESCRIPTION OF SYMBOLS 1 ... Vehicle, 3 ... Drive wheel, 5 ... Forward / reverse switching device, 6 ... Continuously variable transmission, 9 ... Crankshaft, 24 ... Hydraulic pump, 42, 44, 45, 46 ... Oil path, 43 ... Accumulator, 55 ... Hydraulic control device, PriIn, SecIn, CBIn ... Supply side solenoid valve.

Claims (6)

A power transmission device configured to control at least one of a torque capacity and a gear ratio by a hydraulic pressure supplied via a hydraulic pressure supply path, and a hydraulic pump that generates an original pressure of the hydraulic pressure supplied to the power transmission device And a hydraulic control device having an accumulator that selectively performs accumulation of hydraulic pressure generated by the hydraulic pump and release of hydraulic pressure,
Permission to permit control to accumulate discharge hydraulic pressure of the hydraulic pump in the accumulator when the hydraulic pressure supplied to the power transmission device does not change even when control for accumulating the discharge hydraulic pressure of the hydraulic pump is started in the accumulator A hydraulic control device comprising means. When starting control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator, it comprises a judging means for judging whether or not the hydraulic pressure supplied to the power transmission device changes,
The permission means determines the discharge hydraulic pressure of the hydraulic pump when the hydraulic pressure supplied to the power transmission device does not change even when control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator is started. 2. The hydraulic control apparatus according to claim 1, further comprising means for permitting control for accumulating pressure in the accumulator.   When the control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator is started, the control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator is prohibited when it is determined that the hydraulic pressure supplied to the power transmission device changes. The hydraulic control device according to claim 2, further comprising a prohibiting unit.   A valve for opening and closing the hydraulic pressure supply path is provided, and when the hydraulic pressure supply path is opened by the valve, the determination unit starts control for accumulating discharge hydraulic pressure of the hydraulic pump in the accumulator. The hydraulic control device according to claim 2 or 3, further comprising means for determining that the hydraulic pressure supplied to the power transmission device changes.   A valve for controlling the flow rate of the pressure oil passing through the hydraulic pressure supply path is provided, and the permission means is supplied to the power transmission device even when control for accumulating the discharge hydraulic pressure of the hydraulic pump in the accumulator is started. Means for permitting control to accumulate the discharge hydraulic pressure of the hydraulic pump in the accumulator when the flow rate of the pressure oil passing through the hydraulic pressure supply path is controlled by controlling the valve so that the hydraulic pressure does not change. The hydraulic control device according to claim 1, comprising:   The power transmission device is provided between the engine and the drive wheel in a vehicle having an engine that generates power by combustion of fuel and a drive wheel connected to the engine to transmit power, An engine output shaft and the oil pump are connected so that power can be transmitted, and when the vehicle is coasting, fuel cut control is performed to stop fuel supply to the engine. The kinetic energy is transmitted to the hydraulic pump via the output shaft of the engine, and control is performed to drive the hydraulic pump. During cut control, the discharge hydraulic pressure of the hydraulic pump driven by the kinetic energy of the vehicle is accumulated in the accumulator Hydraulic control device according to any one of claims 1 to 5, characterized in that it includes means for permitting the control that.

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